Rotary explosive-engine.



6 SHEETS-SHEET1.

Patented Apr. 1, 1919;

H. L. WEED.

ROTARY EXPLOSIVE ENGINE.

APPLICATION FILED SEPT.7-19l5- H. L. WEED.

ROTARY EXPLOSIVE ENGINE.

APPLICATION FILED SEPT. 1. 1915.

1 ,298 83 a Patented Apr. 1, 1919.

6 SHEETS-SHEET 2.

A TTORNEW H. L. WEED.

ROTARY EXPLOSIVE ENGINE.

APPLlCATtON FILED SEPT. 1'. 1915.

Pafented Apr. 1,1919.-

6 SHEETSSHEET 3.

l/VVE/VTOR //0wa/"d LM eeaf By f 9 WITNESSES:

A TTOR/VEY? H. L. WEED.

ROTARY EXPLOSIVE ENGINE.

APPLICATION FILED sEPT. 7. 1915.

1,298,838, v Patented Apr. 1,1919! 6 SHEETS-SHEET 4- WITNESSES: l/V V511 TOR WMDW H. L. WEED.

ROTARY EXPLOSIVE ENGINE.

APPLICATION FILED SEPT. 1. 1915.

1 ,298,838, Patented Apr. 1, 1919:

6 SHEETSSHEET 5.

WITNESSES: iQ Q nvmvron Howard H. L. WEED.

ROTARY EXPLOSIVE ENGINE.

APPLICATION FILED SEPT. I. 1915 Patented Apr. 1,1919. 6 SHEETS-SHEET 6 [NVEN TOR. Aonmra/ L .M ZKO 24 rozemsy WITNESSbS.

HOWARD L. WEED, OF DETROIT, MICHIGAN.

ROTARY EXPLOSIVE-ENG-INE.

Specification of Letters Patent.

I Patented Apr. 1, 1919.

Application filed September 7, 1915. Serial No. 49,153.

To all whom'it may concern:

Be it known that I, HOWARD L. WEED, a

citizen of the United States, residing at Detion at the intake to the casing. Fig. 5 is a section on the line. 5-5 of Fig. 1. Fig. 6 1s a fragmentary radial section showing the troit, in the county of Wayne and State of admission passages leading to the cylinder Michigan, have invented a new and useful Rotary. Explosive-Engine, of which the following is a specification.

The present invention has reference to an internal combustion engine of the rotary alternating piston type, and among its important features are the following: means whereby the explosive mixture (cool because of evaporation of the gasolene or other bydrocarbon) is used to cool the walls of the combustion or annular Working chamber, and after being itself warmed, to warm the Walls of the intake chamber; means whereby a portion of the chamber is subjected to the cooling action of lubricating oil; means for forming a jacket for the circulation of air or water whereby the oil itself, together with the cylinder,.is cooled; means for effectually sealing thejoints between the rotors and the wall of the annular working chamber; means for sealing the oint between the sections of the casing; means tending to.

equalize the temperature on the various portions of the sealing means; means for bolding the piston rings; countershafts, and eccentric gears thereon meshing with other gears fixed on the rotors for correlating the motions of the combined pistons and abutmen'ts; also means for utilizing the exhaust current of expelled gases between adjacent pistons for scavenging the residual or unexhausted gases from the space between the forward one of the two pistons mentioned and the next preceding piston; and means for thereafter utilizing the further current of burned gases caused by the approach of the rearmost to the foremost of the first mentioned pistons to cause a current of fresh air to pass through and cool the said foremost piston. It is clear that several of these features are applicable to engines other than the internal combustion type, and to other machines. The invention further consists in the details of construction shown, described and claimed.

In the drawings, Figure 1 is a longitudinal section through a preferred embodiment of the invention. Fig. 2 is a similar section on the line 2-2 of Fig. 3. Fig. 3 is a section on the line 3.3 of Fig. 2, parts being broken away. Fig. 4 is a fragmentary radial secor combustion chamber. Fig. 7 is a section on the line 77 of Fig. 2. I Fig. 8 is an -enlarged radial section showing the packing for sealing the joint between one of the rotors and the wall'of the working cham-v ber. Fig. 9 is a fragmentary perspective view showing the joint between the ends of the sealing rings. Fig. 10 is a transverse section through one of the rotors. Fig. 11 is a side View, parts being broken away, of one of the rotors. Fig. 12 is a section on the line 1212 of Fig. 11. Fig. 13 is a diacylinder 3 (circular in radial cross-section) and each of the latter having bearings t for the main engine shaft 5 that may be held from longitudinal movement by the collar 6 and fiy-wheel 7. Loosely mounted on the engine shaft in opposed relation to one another are the sleeves 8 and 9, to which the disks 10 and 11 of the rotors are respectively secured by the bolts 12, or otherwise. Betweenthe disks and loose upon the engine shaft is a packing and friction reducing disk 15 having an outer substantially flat portion or ring 16 against which the flat angular surfaces 18 on the rotor-disks directly engage to form tight joints. Each of the rotors includes a pair of piston blocks,

the members of the corresponding pairs becasing are provided, at diametrically opposite points, withbearings 22 and 23 in which are mounted the countershafts 24 and 25, the former corresponding to the rotor 1019 and'the latter to the rotor 1120. Each of the shafts 24: has rigid therewith an eccentric gear 28, preferably asymmetrical elongated gear with its center of rotation (that is, the center of the corresponding counter-shaft) on the'longest diameter; and the shafts 25 carry similar gears 29, the corresponding parts of which are, however, arranged at 180 to those of the gears 28. Meshing with the gears 28 is the gear 30 integral or otherwise rigid with the sleeve 8, and a simllar gear 31 on the sleeve 9 meshes with the eccentric gears 29. Also keyed to the several.

countershafts are the gears 32 that mesh with and drive the gears 33 fixed on the engine shaft .5.

Referring now more particularly to Figs. 4 and 5, and also to Figs. 1, 2 and 3, it w1ll be seen that the intermediate sections 1 of the casing are provided with radial walls 35 and with annular walls 36 that'form, in conjunction with the cylinder walls 3 and the transverse wall 38 (Fig. 5), passages 39 to which a combustible gas (preferably from an ordinary carbureter, not shown) is admitted from a pipe 40. This gas passes circumferentially about the outside of the cylinder wall, as indicated by the arrows in Figs.

3 and5, and enters the cylinder at points adjacent the wall 38 through the ports 41,

and (see also Fig. 6), after passing through .and being burned in the cylinder in a manner hereinafter described, is finally discharged through the exhaust port 42. (Figs. 2 and 3). I

Each of the pistons 19 and 20 includes at both its forward and rear ends a head or ring carrier 43 (Figs. 3, 11 and 12) having an annular groove 44in which is located an annular spring piston ring 45 that has its ends spaced from each other a distance corresponding to the combined-thickness of the two rotor disks plus that of the portion 16 of the disk 15 (Fig. 12) Pivotally mounted in the ring carrier at 46 is an arc-shaped resilient member 48 havingits free end bearing on the bottom of the groove 44 and'having a shouldered portion 49 conforming to and in close engagement with the peripheral surfaces of the opposed rotor disk and the disk 15. .There is thus formed a tight seal between the piston and the wall of the cylinder and also between the piston and the peripheral surfaces of the opposed rotor disk and the disk 15. The ring carriers may be secured to the piston blocks 19 and 20 by means of the screw bolts 50 (Fig. 3), the latter preferably being retained in posi tion by the set screws 51 and interposed copper or other soft plugs 52. Dowels or pins 53 (Fig. 11) prevent rotation of the ring carriers about the corresponding bolts. It

also has an outer longitudinal groove 56 and 57, the purpose of which will be indicated later.

Between the ends 2 and the walls 35 the intermediate members of the casing include the circumferential cooling passages 60, and, between the walls 35, 36, 3 and the circumferential wall 61'are formed the air passages 62. Both of these passages are supplied with air or other cooling fluid through the inlet 63 (Figs. 2, 5 and 7) which divides and passes around to the opposite side of the casing and escapes through the outlet 64, as shown by the arrows. Passages 66 (Figs. 3 and 7), but one of which is shown, lead from the passages 62 into the cylinder at points in alinement with the grooves 57 in 68 enters the cylinder in alinement with the grooves 56 in the piston blocks. The passage 68 communicates with the exhaust pipe 69 through an annular slot 70 that surrounds the end of a thimble 72 into which the ex-- haust port 42 opens.

As best shown in Figs. 2 and 3, spark lugs 75 are inserted in thewall of the comustion'chamber at points removed substantially 180 from the intake ports 41.

The joint between the intermediate sections of the casing may be sealed in various ways, that shown (which consists of the tongues 76 which are received in corresponding grooves) being deemed preferable.

The manner of sealing the joints between the rotor disks and the cylinder wall is indicated in Figs. 1, 2, 8 and 9. As shown therein, the walls of the intermediate casing sec tions are extended radially inward from the walls 61 at 78 and terminate in the cylindrical flanges 79, these members forming two sides of the annular pockets having their outer surfaces cylindrical for substantially half their depths (designated 80 in Fig. 8), the other half flaring inwardly to the rotor disks at 81. Seated within the pockets are ring carriers, each of which ineludes the base 82, the inner flange 83, the

the surface 81, is interposed between the flanges 83 and 85. It will be understood that the resiliency of the springs is such as to normallyholdthem in rather close engagement with the surface 80-8'1.' outer edge of the flange 85- is preferably grooved circumferentially at 92.

In order to secure a relatively large area The ' of contact for the combustible mixture and air against the walls of the passages 39 60 and 62, ribs 94, 95 and 96 of appropriate form are provided. These ribs also serve to greatly strengthen the casing. It will be understood that the gear cavity in the easin is filled with lubricating oil to a consi erable depth. 1

It will be particularly noted that the eccentric gears on the countershafts determine and govern the acceleration and retardation of the rotors as well as determine the location of inlet and outlet ports of the engine; and that the contour of these gears determines the degree of compression that may be obtained with a given length of pistonmeasured on the circumference of the cylinder.

The pitch line of the eccentric gears may bedetermined empirically. The center of rotation of the large or elliptical gear (on the rotor disk) is, of course, located at its actual centerin other words, at the intersection of its longest and shortest diameters. It is necessary that the pitch line of this large gear be exactly double the length of the pitch line of the eccentric gear.

For a trial determination, draw the straight line AB (Fig. 13) upon which 10- cate the points G and C, at a definite dis tance apart. Lay ofi Gan at a known ratio to C00 (say 1: 1). Lay ofl' Cy greater than Cw approximately in the ratio of 5:2. At a point H midway between the points at and 3 erec't the perpendicular E l-IE. Construct about the point H as a center the symmetrical curve azzEy E with the axis my somewhat greater than the axis EE.

With a pair of dividers subdivide the semi-circumference mEy into a number of parts, say forty or fifty parts, the chords and the arcs of said parts being so nearly equal that the errors can be disregarded. The parts or subdivisions may be assumed to be equal. In the illustration ten subdivisions are used. From the point C (which is to be the center of revolution for the eccentric gear) draw the straight lines 1' 1' oa -r to the ten points of subdivision of the arc acEy. With C as a center, using the ten radii r 1' 1' strike arcs intersecting the line AB at the points 1, 210. Using C as a center strike arcs from the points X 1, 210 intersecting the line DF (which is perpendicular to AB through C Beginning at the pointaz using the maintained distance between the points of the dividers, step 01f with said dividers the points P P P -P which locate themselves upon the last mentioned arcs intersectin DF. If it is found that the last point 10 does not fall on the line DF then the distance Cy can be increased or diminished as the case may require and the trial process repeated until the point P does fall at the intersection of its respective arc wlth the line DF. Now by joining the pomts P I b the curved lme as indicated in the sketc one fourth of the pltch line of the larger gear is determined, and by reproducing this curve for'the other three quarters of the gear the entire pitch line is obtained. In practice the gears produced by .this'method have run .substantially as accurately and as silently as the ordlnary circular gears.

Operation.

The rotors turn clockwise (Fig. 3). As stated, the combustible mixture which enters the casing through the pipe 40 is drawn circumferentially along the passage 39 and into the cylinder through the orts 41. The gears 2829-30-31 are so re ated as to cause the forward piston ring of the rearmost of any given pair of adjacent pistons to pass the passages 66-68 before the mixture is admitted into the space between this and the preceding piston; and for some time thereafter the speed of the forward piston is considerably greater than that of the'rear piston, thus giving rise to the suction necessary for drawing in the charge- When, however, the forward end of the rear p1ston passes the ports 41, the condition becomes reversed, and for a considerable period thereafter the rear piston gains on the forward piston, which results in a compression of the combustible mixture. As the charge passes the spark plugs the firing takes place, but it is preferable, at least in certain instances, to fire only after the point of maximum compression has been passed. The expansive force of the burning gases, because of the increased leverage of the forward piston on the engine shaft at this period, over that which is afiorded the rear p1ston, now causes the former to travel for- A ward at relatively high speed and imparts rotation to the engine shaft. At the same time, the rear piston travels slowly forward. The shape of the gears 2829 is such that this condition exists for a considerable time, thus insuring a relativel long workin stroke with consequent e ciency in the utllization of the expanding gases. The port 42' being uncovered, the exhaust takes place through the thimble 72 andpipe 69.

Considering now the forward piston of the pair under discussion together with the piston that precedes it, the parts will be about in the position shown in Fig. 3, from which it will be seen that the passage 66 is uncovered to admit air between the two pistons, which, together with the aspirating effect of the exhaust gases, induces a How of air through that portion of the cylinder and the passage 68. There is thus secured a complete scavenging of the cylinder just prior to the introduction of the new charge.

Again referring to the foremost of the pair first under discussion, it is clear that the passages 57 come into registration with the passages 66 very shortly after the termination of the scavenging action described. The current of. fresh air is thereupon drawn through the grooves in the piston ring carriers and discharged through the passage 68, thus cooling the parts and preventing undue expansion.

While the operation has been traced, for the most part, with reference to but one pair of pistons, it is clear that the same action takes place at an earlier or later time between the members of each adjacent pair; in other words, the leading piston of any given pair becomes the following (or slowmoving piston so far as the working and intake portions of the stroke are concerned) when considered with reference to the next preceding piston. Thus, in the embodiment shown, four working impulses or strokes are secured for each complete rotation of the rotors.

It is clear also that, by properly proportioning the gears 3233, the speed of the engine shaft may be reduced or otherwise varied in respect to that of the rotors.

The manner of seali the joints between the pistons and the cy inder and between the pistons and the olpposed rotor disks has been pointed oiit.- eferring now to the joints between the rotors and the cylinder:

a certain amount of leakage may occur b'etween the ring 91 and the surface 81 (Fig.

8), and this gas may reach the oove 92. One component of its pressure t rusts the carrier 8283-8485 against the corresponding rotor disk sufliciently to maintain a proper seal between the flat surfaces of contact. It will be noted that a similar action is caused by the resiliency and inclined surfaces of the packing rings. Such gas as escapes into'the groove 92 merely pushes the ring 88 ,over against the flange 84 without affecting the engagement of the rin 88 with the cylindrical surface 80.. The t of the parts is loose enough to allow the ring carrier and rings to be carried around in the pockets, a feature of considerable importance, since the difference in temperatures between the zone of ignition and the zone of intake is sufiicient to set up local stresses that otherwise might cause binding and consequent wear between the flange 83' and the rotor disk. v

The difference in temperature referred to above is much lessened by the circulation of the combustible mixture through the passage 39 (Fig. 5), and local warping of the cylinder wall is thereby largely avoided. At the same time, the temperature of the mixture is raised to a point that insures proper vaporizationand more complete combustion. The heat distribution is also ren- 1,29s,sae

dered more uniform by the flow of air through the passages 62, and by the contlnuous streaming of the oil against the walls 61-7879. ThlS oil also keeps the gears cool, and its excess heat is largely transferred to and dissipated by the flow of air through the passages 60. I

Obviously, skilled designers may change the details of construction within wide limits Without departing from the spirit of my invention, and I do not, therefore, wish to. be limited except as indicated by the subjoined claims.

1. A rotary device comprising a casing, a main shaft mounted therein, said casing including a cylinder, a pair of rotors concentric with and loose on the main shaft, each of 'said rotors including a pair of pistons arranged to travel in the cylinder, at counter shaft for each rotor, an eccentric gear fixed to each counter shaft, a ear r1 'd with each of the rotors and mesliing with the'eccentric gear on 'the corresponding tor, an eccentric gear fixed to each counter shaft, a gear rigid with each of the rotors and meshing with the eccentric gear on the corresponding counter shaft, gears fixed on the engine shaft, and other gears fixed on the counter shaft whereby the gears on the engine shaft are driven, and means for supplying combustible fluid to the space between adjacent pistons, whereby the leading piston is forced forward at a greater rate than the piston next following.

3. A rotary engine comp-rising a casing, an engine shaft mounted therein, said casing including a cylinder, a pair of rotors con centric with and loose on the engine shaft,

each of said rotors including a pair of pis-- ing including a cylinder, a pair of rotors concentric with and loose on the engine shaft, each of said rotors including a pair of pistons arranged to travel 1n the cyl nder, a countershaft for each rotor, an eccentric gear fixedto each countershaft, each of sald gears being symmetrical about two axes at right angles to each other, the correspondlng parts of the two gears be1n g arrangedat 180 to each' other, a gear rigid with each of the rotors and meshin with the eccentric gear on the correspon :ng countershaft, means for driving the englne shaft from the countershafts, and means for supplying propelling fluid to the space between ad acent pistons.

5. A rotary engine comprlslng a caslng an engine shaft mounted therein, said casing 1neluding a cylinder, a pair of rotors concentrio with and loose on the engine shaft, each of said rotors including a palr of pistonsarranged to travel in the cylinder, a countershaft for each rotor, an eccentric gear fixed to each countershaft, each of said gears belng symmetrical about two axes at right angles to each other, the corresponding parts of the two gears being arranged at 180 to each other, the longer axis of each of the gears passing through the center of thecorresponding countershaft, a gear rigid with each of the rotors and meshing with the eccentric gear on the corresponding countershaft, means for driving theengine shaft from thecountershafts, and means for supplying propelling fluid to the space between adjacent pistons.

'6. A rotary internal combustion engine comprising a casing, an engine shaft mounted therein, said casing including a cylinder, a pair of rotors concentric with and loose on the engine shaft, each of said rotors including a pair of pistons arranged to travel in the cylinder, the pistons of the two pairs alternating, means for supplying a charge of combustible mixture to the space between two adjacent pistons, means for igniting the charge, means whereby-the expansion of the charge is thereupon made to force the pistons forward at different speeds, the speed of the forward piston being for a time greater than that of the rear piston, means for causing the rotor of which the forward piston is a part to turn the engine shaft, said casing having an exhaust port which is uncovered by the forward piston as it approaches the end of its relatively faster movement, and means whereby the burned gas escaping through the exhaust port is made to cause scavenging of the space between the forward piston and the piston next preceding, said last namedmeans including an opening through which the remaining gases in said space escape and a separate passage through which air is simultaneously admitted to said space.

7. A rotary internal combustion engine plying a charge of combustible mixture to I the space between two adjacent pistons, means for igniting. the charge, means whereby the expansion of the charge is thereupon made to force the pistons forward at different speeds, the speed of the forward piston being for a time greater than that of the rear.

iston, means for causing the rotor of which t e forward piston is a part to turn the engine shaft, said casing having an exhaust port which is uncovered by the forward piston as it approaches the end of its relatively faster movement, and means whereby the burned gas escaping through the exhaust port is made to cause scavenging of the space between the forward piston; and the piston next preceding, said last named means including an opening through which the regases in said space escape and a separate passage through which air is simultaneously admltted to said space.

8. A rotary internal combustion engine comprising a casing, an engine shaft mounted therein, said casing including a cylinder, a pair of rotors concentric with and loose on the engine shaft, each of said rotors include mg a pair of pistons arranged to travel in the cyllnder, the pistons of the two pairs alternating, means for supplying a charge of combustible mixture to the space between two adjacent pistons, means for igniting the charge, means whereby the expansion of the charge is thereupon made to. force the pistons forward at difi'erent speeds, the speed of the forward piston being for a time greater than that of the rear piston, means for causing the rotor of which the forward piston is a part to turn the engine shaft, said casing having an exhaust port which is uncovered by the forward piston as it approaches the end of its relatively faster movement, said piston having an air passage therein, and means whereby the burned gas escaping through the exhaust ort is made to cause a circula-v tion of air t rough the air passage to cool the piston.

9. A rotary internal combustion engine comprising a casing, an engine shaft mounted therein, said casing including a cylinder, a pair of rotors inclosed by the casing, each of said rotors including a pair of pistons arranged to travel in the cylinder, the pistons of the two pairs alternating, means for supplying a charge of combustible mixture to 12 the space between two adjacent pistons, means for igniting the charge, means where-' by the expansion of the charge is thereupon made to force the pistons forward at different speeds, the speed of the forward piston 30 being for a time greater than that of the rear piston, means for causing the rotor of which the forward piston is a part to turn the engine shaft, said casing having an exhaust port which is uncovered by the forward pis ranged to travel in the cylinder, the pistons of the two pairs alternating, means for supplying a charge of combustible mixture to the space between two adjacent pistons, means for igniting the charge, means whereby the expansion of the charge is thereupon made to force the pistons forward at difi'erent speeds, the speed of the forward piston being for a time greater than that of the rear piston, means for causing the rotor of.

which the forward piston-is a part to turn the engine shaft, said casing having an exhaust passage which'is uncovered by the forward piston as it approaches the end of its relatively faster movement, an air inlet to the cylinder near one side thereof and forward of the exhaust passage, a scavenging passage leading to the exhaust passage from a point opposite the air inlet, the relation of the parts being such that the burned gas escaping through the exhaust passage causes air to flow through the air inlet and the scavenging passage to scavenge the cylinder between the forward piston and the piston next preceding.

11. A rotary internal combustion engine comprising a casing including a cylinder, an

7 engine shaft mounted in *the casing, a plurality of pistons traveling in the cylinder,

- means for supplying combustible mixture to the space between two adjacent pistons, means for igniting the mixture, means whereby the expansion of the gases imparts a forward movement to the forward one of the two pistons, means whereby the last mentioned piston drives the engine shaft, an.

exhaust passage through which the expanded gases are discharged, said cylinder hav- .ing an air inlet at a point forward of the exhaust passage, and means whereby the burned gas escaping through the exhaust passage causes air to flow through the air inlet to scavenge the cylinder between the forward piston and the piston next preceding.

12. A rotary internal combustion engine comprising a casing including a cylinder, an

engine shaft mounted in the casing, a plu rality of pistons traveling in the cylinder,

means for supplying combustible mixture to the space between two adjacent pistons. means for igniting the mixture, means whereby the expansion of the gases imparts a forward movement to the forward one of the two pistons,v means whereby the last mentioned piston drives the engine shaft, an exhaust passage through which the expanded gases are discharged, said cylinder having an air inlet at a point forward of the exhaust passage, the pistons having air passages therein, and means whereby the burned gas escaping through the exhaust passage causes air to flow. through the air inlet and through the piston to cool the latter.

13. A rotary internal combustion engine comprising a casing that includes a cylinder, an engine shaft mounted in the casing, pistons traveling in the cylinder, means, including gears, for transmitting the movement of the pistons to the engine shaft, said casing forming a chamber for the gears, said chamberbeing adapted to receive lubricating oil, and said casing having a circumferential air passage surrounding the gear cllliambler through which air may flow to cool t e oi annular cylinder of circular cross-section, a pair of rotors mounted in the casing co-axial witli the cylinder, said rotors each including 14. In combination, a casing including antherein, said members each being arranged to engage the edge of the other rotor-disk to. form a tight oint.

15. In combination, a casing including an annular cylinder of circular cross-section, a pair of rotors mountedin the casing co-axial with the cylinder, said rotors each including 4 a rotor-disk, the edges of the disks forming part of the wall of the cylinder, each of the rotors alsoinoluding'a piston rigid with the corresponding disk, said pistons having ring carriers, in each of which acircumferential groove is formed, each of the pistons having an arc-shaped sealing member pivoted therein, said members each being arranged to engage the edge of the other rotor-disk I to form a tight joint, and a rotary sealing disk interposed between and co-axial with the rotors, said arc-shaped members also engaging the edge 'of the sealing disk.

16. In combination, a casing including an annular cylinder of circular dross-section, a pair of rotors mounted in the casing 00- cluding a rotof-disk, the edges of the disks forming part of the wall -of the cylinder, each of the rotors also including a piston rigid with the corresponding disk, said pisaxial with the cylinder, said rotors each intons having ring carriers, in each of which groove, said second member having its ends a circumferential groove is formed, each of in contact with the ends of the shouldered 1 the pistons having an arc-shaped sealing portion of the first mentioned sealing memmember pivoted therein, 'the sealing members.

bers each having a shouldered portion that In testimony whereof I sign this specifiextends across the edges of the rotors and is cation.

engaged therewith to form a tight joint, and v V a second arc-shaped sealing member in the HOWARD L. WEED. 

